CN113007052A - 液压轴向活塞机 - Google Patents
液压轴向活塞机 Download PDFInfo
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Abstract
描述了一种液压轴向活塞机(1),所述液压轴向活塞机包括壳体、缸体(2)和阀布置(4),所述缸体(2)以可绕旋转轴线(7)旋转的方式安装在所述壳体中并具有至少一个缸(3),所述阀布置(4)位于所述缸体(2)与所述壳体之间,所述阀布置具有随所述缸体(2)旋转的第一部分(4)和相对于所述壳体固定安装的第二部分。这样的机器将具有高效率。为此,所述第一部分(4)包括可弹性变形的弹簧段(9)。
Description
技术领域
本发明涉及一种液压轴向活塞机,所述液压轴向活塞机包括壳体、缸体和阀布置,所述缸体以可绕旋转轴线旋转的方式安装在所述壳体中并具有至少一个缸,所述阀布置位于所述缸体与所述壳体之间,所述阀布置具有随所述缸体旋转的第一部分和相对于所述壳体固定安装的第二部分。
背景技术
这样的轴向活塞机例如从US10094364B2是已知的。
在轴向活塞机中,所述缸体包括一个或更多个缸,其中每个缸中布置有活塞。每个活塞被连接至活塞瓦,所述活塞瓦靠在斜盘上并借助于保持器装置而被保持抵靠所述斜盘。在一些这样的轴向活塞机中,这些弹簧的另一端推向所述缸体,所述缸体进而推向所述阀布置的所述第一部分或旋转部分。
在任何情况下,为了相对于所述静止部分推动所述阀布置的所述旋转部分,某一力是必需的。当这通过将力从所述缸体传递到所述旋转部分上来实现时,优选地,力的这种传递发生在不同机器中的阀布置中的相同部位处,以避免各个机器之间的性能变化。此外,优选地,力被均匀地分布并具有靠近旋转轴线的中心,以避免接触压力中的局部峰值,以及避免在力以局部接触方式被传递的情况下可能发生的磨损。
发明内容
本发明的基本目的是提供一种具有良好效率的轴向活塞机。
这种目的是通过如开头描述的液压轴向活塞机来解决的,其中所述第一部分包括可弹性变形的弹簧段。
所述弹簧段与所述第一部分形成一体,使得在所述机器的组装期间仅所述第一部分需要被处理。这个位置不需要其它弹簧部件。当所述弹簧段形成在所述第一部分或旋转部分处时,公差可以被保持较小并且相同类型的多个不同机器的所述第一部分可以在相当大的程度上被制造成相同的。
在本发明的实施例中,所述弹簧段围绕所述旋转轴线而布置。这意味着由所述弹簧装置产生的力可以围绕所述旋转轴线而分布。
在本发明的实施例中,所述弹簧段仅在轴向上是可变形的。因而,在径向方向上没有变形,并且在所述弹簧段与所述缸体之间的接触的位置被保持。磨损风险可以被保持为较小。
在本发明的实施例中,力从所述缸体经由所述弹簧段至所述第一部分的传递是关于所述旋转轴线对称的。所述弹簧段将接收来自所述缸体的力。由于所述力,所述弹簧段将在轴向上稍微变形。所述第一部分被设计为补偿轴向未对准,并且因此将与所述阀布置的所述第二部分对准但不与所述缸体的端面对准。因此,所述弹簧段的轴向变形将关于所述旋转轴线稍微不对称。如果由于来自所述缸体的力而导致的所述弹簧的轴向变形大于由于所述未对准而导致的所述轴向变形的不对称性,则接触力的中心将靠近所述旋转轴线并且力从所述弹簧段到所述阀布置的第一部分的其余部分的传递将围绕所述旋转轴线几乎对称。
在本发明的实施例中,所述弹簧段是从所述第一部分中机加工出来的。所述机加工可以例如通过车削来进行。这是将所述弹簧段与所述第一部分的其余部分制成一个部件的简单方式。
在本发明的实施例中,所述弹簧段包括围绕所述旋转轴线且接触所述缸体的凸缘。所述凸缘可以在轴向上相对于所述第一部分的其余部分稍微移动。
在本发明的实施例中,所述凸缘在接触所述缸体的端部处具有加厚段。所述加厚段在所述缸体与所述弹簧段之间提供更大的接触相位,因而降低接触压力,从而降低所述缸体与所述加厚段之间的磨损风险。
在本发明的实施例中,所述凸缘借助于铰链段而被连接至所述第一部分的径向外部部分,其中所述铰链段具有比所述第一部分的厚度更小的厚度。所述弹簧段基本上在所述铰链段中变形。
在本发明的实施例中,所述凸缘具有比所述铰链段的厚度更大的最大厚度。这是将所述弹簧段的变形集中在所述铰链段中的简单方式。
在本发明的实施例中,所述铰链段包括波状形式。所述波状形式允许所述铰链段的变形,其中所述凸缘基本上平行于所述轴向移动。
在本发明的实施例中,所述铰链段在截面图中包括由凸弧状部分连接的两个凹弧状部分。所述凹弧状部分具有位于所述缸体那侧的曲率中心,并且所述凸弧状部分具有位于所述第二部分那侧的曲率中心。所述弹簧段被设计成使得所述弹簧段的轴向变形将不会引起所述缸体与所述凸缘之间大的相对运动。这将使所述缸体与所述凸缘之间的交界面中的磨损最小。
在本发明的实施例中,所述凸弧状部分比所述凹弧状部分中的至少一个凹弧状部分更弯曲。这有助于所述弹簧段的期望的变形。
在本发明的实施例中,所述弹簧段靠在所述缸体的突出部上。因而,所述弹簧段伸出到所述第一部分之外是不必要的。因此,在所述第一部分的机加工期间,较少的材料必须被移除。
附图说明
现在将参考附图更详细地描述本发明,在附图中:
图1示出了轴向活塞机的部件的示意图,
图2以更大的视图示出了图1的细节,和
图3示出了图2的细节的第二实施例。
具体实施方式
图1示意性地示出了轴向活塞机1的多个部件,即具有缸3的缸体2和阀布置的第一部分4。所述第一部分4包括支撑板5和抗磨板6。所述抗磨板6可以由陶瓷材料制成,而所述支撑板5由金属制成。所述壳体和第二部分被省略以简化示图。
在这样的液压轴向活塞机中,活塞(未示出)被布置在缸3中。在操作期间,所述活塞在缸3中上下移动并且所述缸3的自由容积变化。所述活塞被连接至活塞瓦,所述活塞瓦借助于保持器装置而被保持抵靠斜盘。
当所述轴向活塞机1被操作为泵时,被连接至所述缸体2的轴8被旋转。活塞背离所述阀布置移动会将液体抽吸到所述缸3中,活塞朝向所述阀布置移动会使所述液体在高压下移位到外部。
当所述液压轴向活塞机被作为马达操作时,液体被推入所述缸中,从而按压所述活塞远离所述阀布置。如本领域中众所周知的,所述活塞的这种移动与所述斜盘的效应一起产生使缸体2旋转的扭矩。
为了控制所述液体的流量,提供了所述阀布置。
所述阀布置的所述第一部分4必须利用某一力被加载抵靠所述阀布置的第二部分以防止泄漏。
在目前的情况下,这种力通过保持所述活塞瓦抵靠斜盘的保持器系统的弹簧来产生。这些弹簧通常被压缩达几mm。这种大的压缩使所述力对产生公差不敏感。
所述第一部分4(更确切地说支撑板5)包括弹簧段9。所述弹簧段9包括围绕所述轴8和旋转轴线7的凸缘10。所述凸缘10接触缸体2。为此,所述缸体2设置有突出部11。所述突出部11的高度可以相当小。所述高度的尺寸将被设计成在所述缸体2接触所述第一部分4之前所述弹簧段9从所述弹簧段9径向向外地充分变形。
插槽12或止推垫将每个缸3连接至所述第一部分5。每个插槽12借助于O形圈13而被密封在所述缸3中。
图2更详细地示出所述弹簧段9。相同的元件用与图1中相同的附图标记来表示。
所述凸缘10在接触所述缸体2的端部处具有加厚段15。所述凸缘借助于铰链段17而被连接至所述支撑板5的径向外部部分16。所述铰链段17具有比所述支撑板5的厚度更小的厚度。所述支撑板5在除了所述弹簧段9之外具有基本上恒定的厚度。
所述凸缘10具有比所述铰链段17的厚度更大的最大厚度。这意味着所述弹簧段9主要在所述铰链段17中变形,结果是在所述弹簧段9的变形期间,所述凸缘10仅在轴向上移动而不在径向方向上相对于旋转轴线7移位。
所述铰链段17包括两个凹弧状部分18、19,这两个凹弧状部分18、19被凸弧状部分20连接。所述凹弧状部分18、19的曲率中心位于所述缸体2那侧,而所述凸弧状部分20的曲率中心位于所述第二部分那侧。所述凸弧状部分20比所述凹弧状部分18、19中的至少一个凹弧状部分更弯曲,即,所述凸弧状部分20具有更小的曲率半径。
图3示出所述弹簧段9的稍微不同的形式。图1和图2中的相同和相似的部分用相同的附图标记来表示。
在该实施例中,所述弹簧段9同样包括凸缘10。然而,所述铰链段17稍有不同。它仅包括一个凹弧状部分,所述凹弧状部分借助于直边段21而被连接至所述支撑板5的径向外部部分。
通过图2或图3中示出的所述弹簧段9,在所述缸体2与所述阀布置的第一部分或旋转部分4之间实现了稍微柔性接触(compliant/flexible contact),这使得所述缸体2与所述阀布置的所述第一部分4之间的接触力关于所述轴向活塞机的旋转轴线7几乎对称地分布。
所述弹簧段9通过所述阀布置的第一部分或旋转部分4的所述支撑板5机加工(例如车削)而形成。所述弹簧段9关于所述旋转轴线7对称。
所述弹簧段9的一侧将接收来自所述缸体2的力。这是所述凸缘10。由于所述力,所述弹簧段9将在轴向上稍微变形。所述阀布置的旋转部分或第一部分4被设计用于补偿轴向未对准,并且因此将与所述阀布置的第二部分或静止部分对准但不与所述缸体2的端面对准。因此,所述弹簧段9的轴向变形将关于所述旋转轴线7稍微不对称。如果由于来自所述缸体2的力而导致的所述弹簧段9的轴向变形大于由于所述未对准而导致的所述轴向变形的不对称性,则接触力的中心将靠近旋转轴线7并且力从所述弹簧段到所述阀布置的第一部分或旋转部分4的其余部分的传递将关于旋转轴线7几乎对称。
除了有助于提高效率、减少磨损和降低各个机器之间的性能偏差之外,所示实施例具有以下优点:所述弹簧段9可以被设计成使得所述弹簧段9的轴向变形将不会引起所述缸体2与所述凸缘10之间的大的相对运动。对于图2中示出的实施例尤其如此。与例如在所述缸体2与所述阀布置的所述旋转部分4之间放置盘簧相比,这将使所述缸体2与所述弹簧段9之间的交界面中的磨损最小,因为当盘簧轴向变形时盘簧也将径向变形。
此外,不需要向机器添加额外的部件。因此,将不需要生产额外的部件并保持库存,也不会在组装或维修期间可能忘记或不正确地安装额外的部件。
由于所述弹簧段9是从已经可获得的材料机加工的,因此增加的成本被最小化。
Claims (13)
1.一种液压轴向活塞机(1),包括壳体、缸体(2)和阀布置,所述缸体(2)以能够绕旋转轴线(7)旋转的方式安装在所述壳体中并且具有至少一个缸(3),所述阀布置位于所述缸体(2)与所述壳体之间,所述阀布置具有随所述缸体(2)旋转的第一部分(4)和相对于所述壳体固定安装的第二部分,其特征在于,所述第一部分(4)包括可弹性变形的弹簧段(9)。
2.根据权利要求1所述的液压轴向活塞机,其特征在于,所述弹簧段(9)被绕所述旋转轴线(7)布置。
3.根据权利要求1或2所述的液压轴向活塞机,其特征在于,所述弹簧段(9)仅能够在轴向上变形。
4.根据权利要求1至3中任一项所述的液压轴向活塞机,其特征在于,力从所述缸体(2)经由所述弹簧段(9)至所述第一部分(4)的传递是关于所述旋转轴线(7)对称的。
5.根据权利要求1至4中任一项所述的液压轴向活塞机,其特征在于,所述弹簧段是从所述第一部分(4)机加工的。
6.根据权利要求1至5中任一项所述的液压轴向活塞机,其特征在于,所述弹簧段(9)包括凸缘(10),所述凸缘(10)围绕所述旋转轴线(7)并接触所述缸体(2)。
7.根据权利要求6所述的液压轴向活塞机,其特征在于,所述凸缘(10)在接触所述缸体(2)的端部处具有加厚段(15)。
8.根据权利要求6或7所述的液压轴向活塞机,其特征在于,所述凸缘(10)借助于铰链段(17)而被连接至所述第一部分(4)的径向外部部分,其中所述铰链段(17)具有比所述第一部分(4)的厚度更小的厚度。
9.根据权利要求8所述的液压轴向活塞机,其特征在于,所述凸缘(10)具有比所述铰链段(17)的最大厚度更大的最大厚度。
10.根据权利要求7至9中任一项所述的液压轴向活塞机,其特征在于,所述铰链段(17)包括波状形式。
11.根据权利要求10所述的液压轴向活塞机,其特征在于,所述铰链段(17)在截面图中包括由凸弧状部分(20)连接的两个凹弧状部分(18、19)。
12.根据权利要求11所述的液压轴向活塞机,其特征在于,所述凸弧状部分(20)比所述凹弧状部分(18、19)中的至少一个凹弧状部分更弯曲。
13.根据权利要求1至12中任一项所述的液压轴向活塞机,其特征在于,所述弹簧段(9)靠在所述缸体(2)的突出部(11)上。
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DE1006262B (de) * | 1954-11-24 | 1957-04-11 | Georg Wiggermann | Einrichtung bei mehrzylindrigen OElpumpen mit umlaufendem Zylinderkoerper |
US2737666A (en) * | 1955-02-14 | 1956-03-13 | Rockwell Spring & Axle Co | Coil spring retainer and assembly |
FR1233394A (fr) * | 1959-08-24 | 1960-10-12 | Austin Motor Co Ltd | Pompe ou moteur rotatif du type à pistons axiaux |
US3295460A (en) * | 1964-12-21 | 1967-01-03 | Tom H Thompson | Valve plate mounting for a cylinder and multi-piston type pump |
JPS5818074U (ja) * | 1981-07-28 | 1983-02-03 | 三菱重工業株式会社 | アキシヤルプランジヤポンプ又はモ−タ |
JPS58128477A (ja) * | 1982-01-25 | 1983-08-01 | Hitachi Constr Mach Co Ltd | 液圧回転機 |
DE3213031A1 (de) * | 1982-04-02 | 1983-10-06 | Gerb Gmbh & Co Kg | Vorrichtung zur sicherung der federenden von stahlschraubenfedern in federkoerpern gegen abheben |
JP3386463B2 (ja) * | 1992-01-15 | 2003-03-17 | キャタピラー インコーポレイティド | シールドバーレルプレートを備えたアキシャルピストン流体移送装置 |
DE4341850C2 (de) * | 1993-12-08 | 1996-10-02 | Danfoss As | Hydraulischer Axialkolben-Motor |
JP2729770B2 (ja) * | 1995-04-03 | 1998-03-18 | 三愛工業株式会社 | シーツロール機用ばね |
DE10223844B4 (de) * | 2002-05-28 | 2013-04-04 | Danfoss A/S | Wasserhydraulische Maschine |
EP1705372A1 (en) * | 2005-03-11 | 2006-09-27 | Innas B.V. | Variable pump or hydraulic motor |
JP2007327433A (ja) * | 2006-06-08 | 2007-12-20 | Toyota Industries Corp | 可変容量型圧縮機 |
DE102008060067B4 (de) * | 2008-12-02 | 2017-11-02 | Robert Bosch Gmbh | Axialkolbenmaschine mit einer Steuerplatte, die in einem Teilbereich des äußeren Dichtstegs eine erhöhte Elastizität aufweist |
DE102013205263A1 (de) * | 2013-03-26 | 2014-10-02 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine in Schrägscheibenbauart |
US20160273525A1 (en) * | 2013-11-13 | 2016-09-22 | Eco-Sistems Watermakers, S.L. | Hydraulic axial piston pump having a floating rotatory drum |
DE102014225497A1 (de) * | 2013-12-20 | 2015-06-25 | Robert Bosch Gmbh | Hydrostatistische Axialkolbenmaschine |
US10094364B2 (en) * | 2015-03-24 | 2018-10-09 | Ocean Pacific Technologies | Banded ceramic valve and/or port plate |
KR20180093039A (ko) * | 2015-12-10 | 2018-08-20 | 바스프 에스이 | 코일 스프링을 위한 스프링 지지체 |
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